Metering pump



METERING PUMP 4 '75 az 45 7J 69 57 a u I 6o sa e! 4 4J 46 l j? Je l. 6+ 2? /5 es C- R. ALDEN METERING PUMP May 2, 1939.

Filed Feb. 5, 1957 5 Sheets-Sheet 2 ON w, wn a m, w mm m v v r NWA N PERCENT VOLUMETEIC EFFICIENCY May 2, 1939- c. R. ALDEN 2,156,933

METERING PUMP Filed Feb. 5, 1937 5 Sheets-Sheet 3 NVENTOQ PERCENT MAXIMUM ENGINE. SPEED@ I I u i, -cfmoflgys C. R. ALDEN llVIay 2, 1939.

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C. R. ALDEN METERING PUMP May 2, 1939.

Filed Feb. 5, 1957 5 Sheets-Sheet 5 Patented May 2, 1939 nmTEmNG PUMP u. Carroll lt. Alden, Detroitflllich., assignor to Ex- Cell-O C011 gan ration a corporation of Michi- Appuuon February s. 1937, serial No. 124,220

-24s claims. (ci. 12s-14o) The present invention relates to improvements in metering pumps, and particularly pumps for injecting fuel into internal combustion engines.

One of the'objects of the present invention is to provide a metering pump having novel means for automatically controlling the quantity of fuel injection for any predetermined selective engine speed over the speed range.

Another object is to provide'a metering pumphaving new andimproved means for automatically controlling the starting point of injection relative to the engine piston position in response to various selective engine operating speeds.

A further object resides inthe provision of.

' novel means for automatically limiting the maximum quantity of fuel that can be injected during any one pump cycle'at any operative engine speed so that the ratioof ayailable air to fuel cannot fall below a predetermined adjustable minimum necessary for eilicient combustion.

A more speciiic object resides in the provision, in a metering pump having a control valve, of a novel speed control governor 'whichl is operable to adjust the valve to maintain a predetermined Vengine speed, and which is adjustable at will to maintain di'erent selective speeds; also a timing control governor which is operable to adjust the valve to vary the timing of injection, for example, the starting point, in accordance with changes in engine speed, andwhich is adjustable at will to obtain different timing characteristics; also maximum quantity control means responsive to the engine speed for limiting the adjustment of the valve by the speed control governor to limit the maximum quantity of injection in accordance with the volumetric eiliciency of the engine.

Still another object is to provide control means of the foregoing character which is relatively compact, simple and inexpensive in construction, and which is sensitive and reliable in operation.

A further object resides in a modified form in which the speed control governor is of the pneumatic type operable in response to thel air-intake pressure of the engine.

Still another object resides in a second modied form in which the engine speed over the idling or low-speed range isunder the control of a pneumatic governor, and over the high-speed range is under the control of a centrifugal gov- .ernon A further object resides in the provision of novel means automatically operable to compensate for differences in pump leakage at different speeds.

Other objects and advantages will become apparent as the description proceeds.

In the accompanying drawings, Figure 1 is a view partially in plan and partially in longitudinal section of a pump embodying the features of my invention.

Fig. 2 is a longitudinal generally vertical sectional view of the pump,

Fig. 3 is a transverse generally vertical sectional view taken substantially along line 3--3 of Fig. 2.

Fig. 4 is a transverse generally vertical sectional view taken substantially along line 4 4 of Fig. 2. t

Fig. 5 is a partial generally vertical sectional view taken along line 5 5 of Fig. 2.

Fig-6 is a transverse sectional view taken along line 6 6 of Fig. 2.

Fig. 7 is a fragmentary detail view illustrating the speed control governor. f

Fig. 8 is a fragmentary detail view of the timing control governor.

Fig. 9 is an enlarged detail view of a cam for controlling the maximum quantity of fuel injection at different speeds.

Fig. 10 is a diagrammatic representation comparing the volumetric eiiiciency of the engine and the pump delivery per stroke at various operating speeds.

Fig. 11 is a view generally similar to Fig. 2, but of a modied form of the invention in whichk the speed control governor is of the pneumatic type operable in response to manifold pressure.

Fig. 12 is a fragmentary plan view of a detail of the construction illustrated in Fig. 11.

Fig. 13 is a view similar to Fig. 11, but of another modied form of the invention in' which the quantity of fuel injection over different ranges of engine speed is controlled respectively by a pneumatic governor and a centrifugal governor.

Fig. 14 is a fragmentary sectional view of the centrifugal governors embodied in the form of Fig. 13.

While the invention is susceptible of various modifications and alternative constructions, I

have shown in the drawings and will herein describe in detail the preferred embodiment, but

it is to be understood that I do not thereby intend to limit the invention to the specic form disclosed, but intend to cover all modications and alternative constructions falling within the spirit and scope of the invention as expressed in the appended claims. y

Referring more particularly to the drawings,

the invention is illustrated in Figs. 1 to 9 as embodied in a timed metering and distributing pump having means for -automatically controlling the speed-delivery characteristics. In its broad aspects, the invention, however, is not limited to 5 the particular type of pump shown, but may be adapted to various types of timed metering pumps.

-The pump, 'f constituting the exemplary embodiment of the invention, comprises a main housing or body I5, one end of which is 'closed by a mounting plate I6 adapted to be secured to any desired part of the block of an internal combustion engine (not shown), and the other end oi' which is provided with an open sleeve I1 having an internal annular flange deiining an outwardly` facing shoulder I8. A pump drive unit I9 is located in the closed end of the housing I5, and a self-contained hydraulic unit 20, including the closely tting precision parts for metering a0 and delivering the fuel, is removably inserted into the sleeve I1 in position against the shoulder I8 for operative association with the drive unit. To facilitate a ready understanding of the invention, the detailed construction of the hy- 2li draulic and drive units I9 and 20 will rst be described.

The self-contained-hydraulic unit (see Figs. 2 and 6) comprises a plurality of parallel annularly arranged reciprocatory pump plungers 2|, 3o six in the present instance, which extend slidably into a like number of cylinders 22 formed in and opening to the inner end of a stationary body 23. Individual discharge lines or tubes 24 (one shown), for. delivering the metered charges of fuel to the engine, are connected respectively to the closed ends. of ythe pump cylinders 22 by means of valve iittings 25 threaded into the end of the body 23. A spring-seated check valve 26 is provided in each of the fittings 25 to prevent a reverse flow from the associated discharge line to the corresponding cylinder, and to close against the low pressure of the fuel supply. Preferably, the body 23 is cylindrical, and is provided at its inner end with an external peripheral ange 21 having a sliding t in the sleeve I1 and adapted unit 2|! with the drive unit I9. A spline pin 28, projecting radially from the body 23 into a straight longitudinal groove 29 in the sleeve I1, serves to locate the hydraulic unit 20 in the proper angular position. A ring nut 3B is freely rotatable on the body 20 'against the flange 21, and is removably threaded into the sleeve I1 to clamp the hydraulic unit 2li in position.

The metering and timing of fuel injection is under the control of a single rotary valve member 3| which is mounted for rotation and axial adjustment in a valve bore 32 opening through the body 23 centrally of the cylinders 22. A plurality oi' inlet and by-pass ports 33 open in a common transverse plane from the periphery of the valve bore 32 respectively to the closed ends of the cylinders 22, and are never closed or sealed by the plungers 2 I. The valve rotor 3| is formed intermediate its ends with a peripheral low pressure fuel supply and relief belt 34 which d in the plane of the ports 33 is interrupted only by a longitudinally extending land 35 in bearing engagement with the bore 32. An annular groove 35, formed in the bore 32, is always in communication with the belt 34, and is connected through a fuel inlet passage 31 to a line or tube 38 leading from a suitable source of fuel supply, such, for example, as a primary pump 39 u mountedon the underside oi the housing I5.

to engage-the shoulder lil-to align the hydraulic The supply line 3811s connected by means of a screw fitting 40 removably threaded into one side of the body 23.

It will be understood that the pump plungers 2| are reciprocated in overlapping uniform sequence, and that the valve member 3| vis rotated in timed relation thereto. The valve member 3| is so timedthat the land 35 in its successive movement across the ports 33 will close each port during a predetermined portion of the pressure stroke of the'associated pump plunger 2|. 'I'he trapped fuel displaced by the plunger isdelivered to the associated discharge line 24 for injection into the engine. During the remainder of the pressure stroke, before and after injection, the fuel displaced by the plunger 2l is returned through the associated port 33 to the belt 34, and during the suction or return stroke fuel is supplied to the associated cylinder 22.

The width of the land 3 5 in the plane of the ports 33 determines the quantity of metered injection. To provide for quantityadjustment, the land 35 is tapered longitudinally,A and preferably is triangular in shape. Dependlngvon the direction of the controlling side edges of the land 35,

either the starting point of injection, or the end point thereof, or both, may be variable upon axialadjustment of the valve members 3| for quantity control.

The pump plungers 2| and the valve member 3| project into a cup-shaped enclosing shell 4| and are aligned with openings in the transverse wall 42 thereof. The rim of the shell 4| is suit-v ably bolted against the inner end of the body 23. Coiled compression springs 4 3 encircle the projecting ends of the plungers 2| and constitute the means for urging the plungers outwardly of the cylinders 22 in the suction stroke. 'I'he springs 43 abut at one end against the cylinder body 23,

and at the other end respectively against cupshaped retainer members 44 anchored to abutment heads 45 on the outer ends of the plungers 2|.

The hydraulic unit 20, is brought, as an incident toits insertion into the housing I5, into separable association with the drive unit I9, and the latter is operable to reciprocate the-plungers 2| and rotate the valve member 3| in proper synchronism, as described. Referring now to the detailed construction of the drive unit I9, the housing I5 is formed intermediate its ends and in spaced relation to the mounting plate I6 and the hydraulic unit 20 with a transverse wall centrally enlarged to constitute a tappet body 45. A plurality of tappets 41 are reciprocably mounted in bores 48 opening through the body 46, and are in axial alignment respectively with the pump plungers 2|. Each tappet'41 is formed in one end with an axial bore 49 terminating with a socket 50, and on the other end with a ball head5l. Similar sockets 52 in opposed relation to the sockets and.accessible through the openings in the wall 42 of the shell 4| are formed in the abutment heads 45 on the projecting ends ofthe pump plungers 2|. A plurality of actuating rods 53, with the opposed'ends rounded and in engagement respectively with the sockets 50 and 52, are operatively interposed between the pump plungers 2| and the respective tappets 41, so that in normal operation each plunger, associated, connecting rod and associated tappet reciprocate jointly.

'I'he tappets 41 ,are reciprocable in uniformly timed relation by a. rotary swash plate 54. More particularly, the ball heads 5I of the tappets 41 are in bearing engagement with sockets 55 formed in a plurality of floating shoes 66v confined on an annular shoe plate 51. by an annular cage or retainer 58. The plate 51 and lshoe 56 assembly is slidably disposed against the inclined face of the swash plate 54. k

The swash plate 54 is rotatably disposed against the mounting plate I6, and is rigidly secured to a` tubular drive shaft 59. "I'he inner end of the shaft 59 is journaled in a bore 60 opening centrally through the tappet body 46, and the outer end is journaled in and extends through a bearing 6| in the mounting plate |6. A gear 62 is removably secured to a hub 63 on the outer end of 'the shaft 59, and is adapted to be connected for a drive from the engine crank shaft (not shown). Hence, the pump plungers 2| will be operated in predetermined phase relation to the engine pistons (not shown).

'I'he valve member 3| is rotatable from the shaft 59 in adjustable timed relation to the reciprocation of the pump plungers 2|. The drive to the valve member 3| (see Figs. 2 and 8) includes an inner tubular shaft 64 which extends through the shaft 59, and which is rigid at its outer end with a coupling sleeve 65 slidable and rotatable in an end enlargement 66 of the bore through the shaft 59. Two diametrically opposed spline pins 61 project radially from the shaft 59 into inclined or helical slots 68 in opposite sides of the sleeve 65. A second coupling sleeve 69 is splined tion therewith and straight-line axial adjustment relative thereto, Fitting into and rigidly connected to one end of the coupling sleeve 69, as by a cross pin 10, is a member 1| having an axially separable rotative drive connection with the valve rotor 3 In the present instance, the member 1| has an end slot 12 slidably receiving a tang 13 on the adjacent end of the valve rotor 3|. kA sleeve 14 fixed on the same end of the rotor 3| has a telescoping fit with the slotted member 1| and the coupling sleeve 69. A coiled compression spring 15 is seated at one end against a hollow screw plug 15I threaded into and closing the pistons is constant; however, the start of injec tion may be advanced or retarded respectively by shifting the coupling sleeve 65 and shaft 64 axially in opposite directionsto effect a corresponding angular adjustment of the valve rotor 3|l relative to the drive shaft 59. These adjustments for volume and timing control are permitted independently of each `other by reason of the spline connection between the shaft 64 and the coupling sleeve 69.

One of the features of the present invention is to control the starting point of injection in accordance with the engine speed, for example, to advance the starting point of injection relative to the position of the engine piston upon an increase in engine speed. In the form of Figs. 1 to 9, the axial position of the shaft 64, and hence its position of rotary adjustment, is subject to adjustment automatically by a timing control governor 16 responsive to the engine speed. More particularly, the governor 16 (see Fig. 8) is of the opposition to an adjustable spring mechanism l 11. Radially extending heels 8`| on the weights 18 bear against the outer end of the coupling sleeve 65, and tend to urge the latter axially in a direction to advance the starting point of injection progressively in response to corresponding increases in speed.

An annular bearing raceway 82 is xed on the shaft 64 for movement therewith, and is disposed adjacent the inner end of the drive shaft 59. Slidably and rotatably disposed on the shaft 64 in opposedrelation to the raceway 82 is a second raceway 83. Suitable anti-friction rollers 84 are located between the raceways 82 and 83 to complete the bearing relationship. A timing lever 85 is pivoted intermediate its ends on a cross pin 86 suitably supported in depending lugs 81 on a governor housing 88 bolted to the top of the housing l5, and has a depending bifurcated end in engagement with the exposed face of the bearing raceway 83 at opposite sides of the shaft 64. The other end of the lever 85 projects upwardly into the governor housing 88, and is acted on by spring means 89 tending to urge the sleeve 65 in a direction to retard the starting point of injection. In the present instance, the spring means 89 consists of two parallel coiled'compression springs seating at one end against two centering projections 90 on the upper lend of the lever 85, and at the other end against two opposed centering projections 9| adjustably threaded into the adjacent wall of the housing 88. It will be evident that the spring mechanism 11 will seek a state of equilibrium with the'governor weights 18 at all operating speeds, and hence the phase relation of injection to engine piston position will vary as determined by the spring means 89in response to speed changes. Different speedphase characteristics may be obtained by adjusting the compression of the spring means 89, as by means of the adjustable projections 9|.

Another feature of the invention resides in controlling the quantity of fuel injection to limit the engine operating speed to any selectively deterininable value within' a suitable range. In the form of Figs. 1 to 9, the axial position of the valve rotor 3| is adapted to be adjusted by an elongated quantity control pin 92 which extends slidably and rotatably throughthe shaft 64, and the inner end of which constitutes an abutment for the slotted member 1| to limit movement of the valve rotor by the spring 15, 'I'he axial position of the pin 92 is subjectv to adjustment (see Fig. 7) by a speed control governor 93 preferably comprising two y ball Weights 95 acting in opposition t0 a manually adjustable spring mechanism 94. More particularly, thefly ball weights 95 are pivotally mounted on xed pins 96 in the end plate 80, and are adapted to swing outwardly in a plane at right angles to that of the weights 18. Radially extending heels 91 on the weights 95 bear against a head 98 on theouter end of theandv axial movement with the coupling sleeve 69. A second raceway is rotatably disposed on the sleeve 69 in opposed relation to the raceway 99,.and anti-friction rollers |0| are positioned between the raceways to complete the bearing relationship. Pivotally mounted intermediate its ends on a cross pin |02 supported in depending lugs |03 on the housing 88 is a three-armed lever |04. One arm of the lever |04 is bifurcated and extends downwardly into engagement with the exposed face of the raceway |00. A lateral arm |06 is engaged by a coil compression spring |01 which tends to revolve the lever |04 against the raceway |00 for idling speed control, and which is seated at its fixed end against an adjustable stop |08 on the inside of the housing 88. The third arm |09 projects upwardly, and is engaged by a coil compression spring ||0 acting in the same direction as the spring 01, and available for variable high speed operation.

It will be understood that the springs 15, |01 and ||0 tend jointly to effect movement of the valve rotor 3| in a direction to increase the quantity of fuel injection, and that the governor weights 95 oppose this movement and set up an equilibrium at an engine speed determined by the spring action. The compression of the spring ||0 is adjustable, under manual control, to vary selectively the speed at which the engine is to operate, and hence this spring and its adjusting means correspond to a speed throttle control.

The end of the high speed control spring H0 remote from the lever arm |09 seats against a centering retainer having a flared socket ||2 in universal bearing engagement with the rounded end of a pin ||3. This pin ||3 is fixed to one end of a pressure applicator in the form of an arm 4 secured to a cross shaft H5 journaled in and extending through bearings ||6 in the side walls of the housing 88. A lever H1 is fixed on one end of the shaft 5 for hand actuation, and a crank arm ||8 is secured to the other end of the shaft for connection to a foot pedal (not shown). Fixed on the arm ||4 is a lug 9 which is movably disposed between two limit stops |20 and |2|. The stop` |20 is adjustably mounted in the housing 88, and defines the maximum speed position The stop |2| defines the inoperative position of the arm ||4, and is yieldable, preferably consisting of a springactuated plunger normally projected against a fixed lug |22. When the arm ||4 is oscillated into position against the stop |2|, the compression of the spring ||0 is relieved, and the idling spring |01, supplemented by the light pressure of the rotor spring 15, assumes primary control of the speed of operation.

The volumetric efficiency of an internal combustion engine varies with speed changes. Referring to Fig. 10, the typical curve A, which represents the volumetric efficiency, shows that less air per cycle is handled at top engine speeds than at lower speeds. The normal fuel delivery of the pump per cycle tends to increase in accordance with the speed as illustrated by the typical curve B.` This is due to the increased effect of yleakage lat low speeds, and to increased effective duration of by-pass port closure at high speeds. As a result, there is likely to be an insuiliciency of fuel to develop maximum torque at the lower speeds, as represented by the space between the curves A and B below '10 per cent.

of the maximum engine speed, and an excess of fuel at the higher speeds, as represented by the lspacebetween the curves A and B abovev '10 per cent. of the maxim engine speed. One of the important features o the presentV invention resides in correcting the fuel delivery, as represented by the curve C, to conform more nearly to the theoretical volumetric efciency of the engine. To this end, means is provided for automatically limiting the maximum quantity of fuel in accordance with the varying'maximum requirements at different operating speeds, regardless of the quantity of fuel that might otherwise be delivered under the existing state of equilibrium between the spring mechanism 94 and the weights 95, to insure that the ratio of available air to the fuel delivered cannot drop below an adjustable minimum previously determined as .desirable for safe and efficient operation.

This limitation is a function of the engine speed, and hence is advantageously subjected to control by the governor 16 acting through the timing lever 85. In Figs. 1 to 9, an abutment or stop collar |23 is freely rotatable and slidable on the coupling sleeve 69 for end engagement with the sleeve 14 on the valve rotor 3|. A bell crank lever |24, pivotally mounted oi a pin |25 supported within the housing 88, has a depending bifurcated arm adapted to engage the right end of the collar |23. 'I'he other arm of the lever |24 carries a cam follower |26 adapted for engagement with a cam |21 on the timing lever 85. In the present instance, the cam |21 (see Fig. 9) is formed on the end of a screw plug |28 removably and adjustably threaded through a lug |29 on the upper end of the lever 85, and is suitably contoured in accordance with the desired characteristics of the curve C so that the fuel limitation will be properly responsive to changes in engine speed. The characteristics of the curve C may be changed at will as desired merely by substituting cams |21 of different contours. The stop collar |23, reacting through the lever |24 on the cam |21, serves as a limit stop for the sleeve 14, and hence limits adjustment of the valve rotor 3| under the influence of the spring 15 in a direction to increase the quantity of fuel injection. Within this limit, normal speed control by the spring ||0 prevails. When the limit is reached, additional movement of the coupling sleeve 69 to the right is permitted by movement of the tang 13 out of its extreme inward position Within the slot 12.

When the restraining force, adapted to be applied through the hand lever or the pedal actuated arm I8, on the speed adjusting arm I4 is released, 'the lug ||9 will engage but not depress the yieldable stop |2|, thereby instituting idling operation. To provide means for stopping injection, the arm ||4 is formed with a finger |30 which is adapted upon movement against the pressure of the stop |2| to engage one arm of a bell crank lever |3| freely pivotal on the pin 86. The other arm of the lever |3| is disposed for engagement with a lug |32 on the lever |24, and upon oscillation by the arm ||4 will actuate the lever |24, independently of the cam |21, to shift the stop collar |23 and thereby the rotor. 3| into the stop position.

In the modied form of Figs. 11 and 12, the quantity of fuel injection is under the control of a pneumatic governor |33 'in balance with and responsive' to changes in the manifold pressure of the engine. Air enters the manifold (not shown) through an inlet duct |34 in which is mounted an adjustable restriction, such as a butterfly valve |35 operable manually in any appropriete manner, as by a foot accelerator. At any given setting of the valve |35. the manifold pressure is responsive to the engine speed. The governor` |33 therefore serves both to vary the quantity of fuel delivered to the engine over a suitable range in accordance with selective adjustments of the valve |35 responsive to manifold vacuum as determined by the opening of the valve' |35 at any given speed. In other material respects, such as the pump per se, the springloaded timing governor and the means for limiting the-maximum quantity of fuel injection in accordance with the volumetric efdciency-speed characteristics of the engine, the modified form is closely similar in construction and operation to the first form. Hence, parts of the modified form are identied without further description by the same reference numerals as the corresponding parts of the first form plus the distinguishing character a.

'The pneumatic governor 33 of Fig. 11 comprises a cylinder |36 which is removably secured in and opens through one side wall of the governor housing 88, and which is closed at the outer end by a cylinder head |31. A suitable passage or tube |38 serves to connect the interior of the cylinder head |31 to the manifold inlet duct |34 at the low pressure side of the valve |35. A fluid pressure responsive element, such as a. piston |39 is slidably disposed in the cylinder |36, and is rigid with an axial rod or bar |40 extending into the housing 88a. Two concentrically disposed coiled compression spring |4| and |42 tend to move the piston |39 outwardly 'of the cylinder |36 against the manifold suction. The fixed end of the spring |4| engages an annular seat |43 secured between the cylinder |36 and the head |31. The corresponding end of the spring |42 extends through the seat |43, and engages an adjustably mounted seat |44 within the head |31. In the present instance, the spring seat |44 is supported on the inner end of a bolt |45 adjustably mounted in a tubular plunger |46 slidable in a 'guide sleeve |41 in the end wall of the head |31.

'I'he sleeve |41 extendsaxially of the piston |39, and is closed at the outer end by a cap screw |48 against which the plunger |46 normally abuts. It will be understood that the aggregate pressure of the springsv |4| and |42 determines the characteristics of the governor |33, and therethrough the desired air-fuel ratio of the combustible mixture. Upon removal of the nut |48, the bolt |45 may be turned to adjust the pressure of the spring |42 and thereby vary the ratio. A crank arm |48 engages the plunger |46, and is operable from the exterior of the head |31 to move the plunger inwardly from the cap |48 when priming is desired. Y

The inner end of the piston rod |40 is pivotally connected to the free end of an arm |50 (see Fig. 12) xed on a pin |5|. This pin is rotatably mounted in the lower end of a lever |52 which the pin |5| for rotary adjustment by the arm |50 is a cam or eccentric |56 which engages a cam follower |51 onv the dependingl arm of the bellcrank lever |24, The lower end of this lever arm engages a` thrust bearing |58 on the coupling sleeve 69B, and therethrough constitutes an adjustable stop determining the axial position of the valve member 3|.

It will be understood that upon movement of the piston |89 to the left in response to an increase in manifold suction, the cam |66 will be adjusted to oscillatethe lever |24*l in a direction to reduce the quantity of fuel injection. Upon a reverse movement of the piston |33,'the quantity of fuel injection will be increased Outward movement of the piston |39 is limited by a stop projection |58 on the arm |50 adapted in one extreme position to engage the underside of the rod |40 and thereby lock the parts against further relative movement. 'Ihe lever |24* is alsov under the control of the cam |21", and, ii the quantity of fuel injection reaches a predetermined maximum for the prevailing speed, will limit further adjustment of the valve rotor 3I. In this event, the cam |56 may separate from the follower |61. If the linut of injection for the prevailing speed has not been reached, the follower |26* may be separated from the cam |21. Injection may be stopped manually by a pull wire |58 extending through a conduit |60 into the housing 88n and connected to the lever |24".

Provision is made for axially adjusting the va'lve member 3|a independently of the governor |33 and in response to certain changes in the engine speed to compensate for the leakage of fuel at the lower speeds and thereby maintain a readily ignitable air-fuel ratio. As a result, the low speed end of the curve C (see Fig. 10) is brought more nearly into coincidence with the corresponding end of the curve A. The means for this purpose comprises a headed member |6| which is adjustably threaded into the timing lever a, and which extends freely through an opening |62 in the upper end of the lever |52. The head of the member |6| is larger than the opening |62, and hence is adapted to oscillate the lever |52 about the pivot |53 in response to movement of the lever 85B in the slow speed range. The cam |56 will thereby be oscillated correspondingly, and independently of adjustment bythe governor |33 to augment the quantity of injection.

The modified form of Figs, 13 and 14 is closely similar to the twovpreceding forms in respect to the construction and ,operation of the pump per se, the timing control, and the maximum fuel quantity control, and is closely similar to the form of Figs. 11 and 12 in respect to the control of the speed in response to the manifold pressure. It is therefore deemed necessary to describe in detail only the essential differences. Parts of the third form are identified by the same reference numerals as corresponding parts inthe first two forms plus the letter b.

The third form comprises a pneumatic governor |33b for controlling the speed in response to the manifold pressure. Governors of this typeV are particularly advantageous in maintaining close speed regulation at low engine idling speeds. At high speeds, closer regulation is obtainable by centrifugal governors. The third-form therefore also comprises a centrifugal governor |63 which ,assumes control at and near maximum speeds.

Referring more particularly to Figa-13 and 14, the cylinder |36J of the pneumatic governor |33 is integral with the housing 88, and the cylinder head |31b is in the form of a plate in which the anchor bolt |45b for the spring seat |44'l is adjustably threaded. The piston |39 is actuated by the single spring |421. In this form, the pin# |5|b supporting the cam |56b is shown mounted higher speeds is also adapted in a position. Manually operable means shaft hub 63h, and engaging the end of a control pin 92h extending slidably through the shaft 64b and coupling sleeve 69" for engagement with the slottedmember 1lb. The governor |63 acts in opposition to spring means |64 interposed between two fingersV |65 on the weights 95h, and at the to be opposed by the spring 15". -2|'.n this form, the weights 95h vare within the hollow timing control weights 18b and in the'same axial plane as the latter.

In operation, the quantity of fuel injection is under the control of the governor |33b which acts through the rod |40", arm |50b, cam |56, lever |20?, bearing |58 and coupling sleeve 69h against the valve rotor 3|h in opposition to the spring 15b. At maximum engine speed, the centrifugal governor |63 assumes control to the exclusion of the governor |331', and will seek a state of balance with the spring l5b to control the axial position of the valve member 3|b. It will be understood that the governor 16b controls the phase relation of the starting point of injection to the engine piston position in accordance with the speed, and that the cam |21b limits the maximum quantity of fuel injection for each speed, in the same manner as do the corresponding parts in the two forms of Figs. 1 to 12.

I claim as my invention:

1. A pump mechanism comprising, in combination, a pump having a rotary metering valve axially adjustable to vary the quantity of pump deliveryfa plurality of parallel reciprocatory pump units annularly arranged about said valve, spring means tending to urge said valve in a .direction to increase said quantity, and drive means for operating said units in timed sequence and for rotating said valve in predetermined phase rela.- tion to said units, a stop element for limiting the position of said valve under the influence of said spring means, means for automatically adjusting said stop element in response to changes in the. operating speed of said pump, and means for automatically limiting the maximum permissible adjustment of said valve in said direction independently of said last mentioned means.

2. A pump mechanism comprising, in combination, a pump having a rotary metering valve axially adjustable to vary the quantity of pump delivery, a plurality of parallel reciprocatory pump units annularlyarranged about said valve, spring means tending to urge said valve ln a direction to increase said quantity, and drive means for operating said units in timed sequence and for rotating said valve in predetermined phase relation to said umts, governor means driven by said pump for effecting axial adjustment of said valve, andmeans defining a limit of adjustment of said `valve by said governor means in said direction and being automatically operable to adjust said limit in predetermined response to changes in the operating speed of said pump.

3. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity of pump delivery, means for automatically adjusting said element in response to changes in the operating speed of said pump, said means being adjustable at will to effect adjustment of said element in relation to said speed, and means operable by said pump for automatically limiting the extent of adjustment of said to' changes in'said speed, and means acting on.

said control means independentlyof said second mentioned means to limit the maximum quantity of pump delivery.

5. A pump mechanism Jcomprising, in combination, a pump having a drive element and having a control element adjustable to vary the quantity of pump delivery and independently adjustable to vary the phase relation of the time of said delivery to the position of said drive element, means for automatically adjusting said control element to vary said quantity in response to changes in the operating speed of said pump, means for automatically adjusting said control element to vary said phase relation in response to changes in said speed, and means adjustable by said last mentioned means for limiting the, maximum quantity of pump delivery.

6. A pump mechanism comprising, in combination, a pump having an axially adjustable rotary metering control valve and a plurality of of parallel reciprocatory pump units annularly arranged about said valve, drive means for operating said of said lever against said abutment to move said Valve shaft in one direction, and centrifugal governor weights rotatable with said drive shaft and acting on'said valve shaft in opposition to said spring means, whereby the angular phase relation of 'said valve to said pump units is made responsive to the speed of Vsaid drive shaft.A

'7. A pump mechanism comprising, in combination, a pump having a rotary metering control valve and a plurality of parallel reciprocatory pump units annularly arranged about said valve, drive means for operating said units in timed sequence and including adrive shaft extending axially of said valve, a longitudinally adjustable valve shaft extending axially through said drive shaft and having slidable spline rotary drive connections with said drive shaft and said valve, one of said connections being helical to eiect an angular phase adjustment of said valve relative to said drive shaft upon axial movement of said valve shaft, a radial abutment on and movable axially with said valve shaft, a spring actuated phase control lever acting against said abutment to move said valve shaft in one direction, and a centrifugal governor weight rotatable with said drive shaft and acting on said valve shaft in opposition to said lever, whereby the angular phase relation of said valve to said pump units is 2,156,988 made responsive to the speed of said drive shaft.

8, A pump mechanism comprising, in combination, a pump having a rotary metering valve and a plurality of pump units controlled by said valve, drive means for operating said units in timed sequence and including a power shaft, means for driving said valve from said shaft and including a slidable helical spline connection for adjusting the angularrelation of said valve to said units, adjustable spring means tending to adjust said connection in one direction, centrifugal means rotatable by said shaft and tending to adjust said connection in opposition to said spring means, means for adjusting said valve axially to vary the quantity of delivery at any speed, a cam movable with said spring means, and means controlled by said cam for limiting the adjustment of said valve in a direction to increase said quantity.

9. A pump mechanism comprising, in combination, a pump having a rotary metering valve axially adjustable to vary the quantity of pump delivery, a plurality of parallel reciprocatory pump units annularly arranged about said valve, spring means tending to urgev said valve in a direction to increase `said quantity, and drive means for operating said units in timed sequence and for rotating said valve in predetermined phase relation to said units, a sto'p element for limiting the position of said valve under the influence of said spring means, a centrifugal governor for controlling the axial position of said valve in response to the operating speed of said pump, said governor comprising a quantity control lever acting against said stop element in a direction to increase said quantity, idling spring means tending to actuate said lever, operating spring means tending to actuate said lever, means for adjusting the force of said operating spring means, and centrifugal governor Weights rotatable by said drive means and acting against said stop element in a direction to decrease said quantity in opposition to said lever, whereby any selective operating speed may be substantially maintained, and means available at will for adjusting said stop element independently of said governor to stop pump delivery. i

10. A pump mechanism comprising, in com bination, a pump having metering valve adjustable to vary the quantity of pump delivery,A a plurality of parallel reciprocatory pump units, spring means tending to adjust said valve in a direction to increase said quantity, and drive means for operating said units in timed sequence and for operating said valve in predetermined phase relation to said units, a stop element for limiting the position of adjustment of said valve under the influence of said spring means, and a centrifugal governor for controlling the position ofy adjustment of said valve in response to the operating speed of said pump, said governor comprising a quantity control lever v acting against said stop element in a direction to increase said quantity, operating spring means tending to actuate said lever,- and a. centrifugal governor weight rotatable by said drive means and acting against said stop element in a direction to decrease said quantity in opposition to said lever. f`

1l. A pump mechanism comprising, in combination, a pump having a rotary metering valve axially adjustable to vary the quantity of pump delivery, a plurality of parallel rciprocatory pump units annularly arranged about said valve,

spring means tending to urge said valve in a direction to increase said quantity, and drive means for operating said units in timed sequence and including a drive shaft extending axially of said valve, a coupling sleeve having an axially separable driving connection with said valve and constituting a stop for limiting adjustment 'of said valve under the inuence of said spring means, a' longitudinally adjustable valve shaft extending axially through said drive shaft and having a slidable straight spline rotary drive connection with said coupling sleeve, a slidable helical spline rotary drive connection between said shafts, a quantity control lever acting against said coupling sleeve ina direction to increase said quantity of pump delivery, idling spring means for actuating said lever, operating speed spring means for actuating said lever, means available at will for adjusting the force of said operating speed spring means, a control pin extending slidably through said valve shaft for end abuttingA engagement with said coupling sleeve, centrifugal governor weights rotatable with said drive shaft and acting on said pin in a direction to decrease said Jquantity of pump delivery, an abutment on and movable axially with said' valve shaft, a timing lever acting against said abutment in a direction to retard the phase relation of said valve shaft to said drive' shaft through vthe action of said rotary spline connection, adjustable spring means tending to actuate said timing lever, centrifugal governor weights rotatable with said drive shaft and acting on said valve shaft in opposition to said timing lever, and

'i means responsive to the movement of said timing lever for limiting the position of said valve ment adjustable with said valve, and a centrifugal governor for controlling the position of adjustment of said valve in response to the operating speed of said pump, said governor comprising a quantitycontrol lever acting against said stop element in a direction to increase said quantity, adjustable operating spring means tending to actuate said lever, and centrifugal means rotatable by said drive means and acting against said stop element in a direction to decrease said quantity in opposition to said lever.

13. A pump mechanism comprising, in combination, a pump having a rotary metering valve axially adjustable to vary the quantity of pump delivery, a plurality of parallel reciprocatory pump units annularly arranged about said valve, .and drive means for operating said units in timed sequence and including a power shaft extending axially of said valve, a coupling sleeve movable with said valve, a longitudinally adjustable valve shaft extending axially through said power shaft `and having slidable spline rotary drive connecf tions' with said coupling sleeve and said powerf shaft, a llever acting against said coupling sleeve in a direction to increase said quantity of pump delivery, spring means for actuating said lever, a

control pin extending slidably,through said valve s shaft for engagement with .said coupling sleeve,

centrifugal means rotatable by said power 'shaft means tending to actuate said 4last mentioned lever, centrifugal means rotatable by said power shaft and acting ,on said valve shaft in opposition to said last mentioned lever, a stop collar axially slidable on and adapted to limit the movement of said valve, and a lever operable by said cam to control the position of said collar.

14. A pump mechanism comprising, in combination, a pump having a rotary metering valve axially adjustable to vary the quantity of pump delivery, a plurality of parallel reciprocatory pump units annularly arranged about said valve, spring means tending to urge said valve in a direction to increase said quantity, and drive means for operating said units in timed sequence and including a. drive shaft extending axially of said valve, a-coupling sleeve having an axially separable driving connection with said valve and constituting a stop for limiting adjustment of said valve under the inuence of said spring means, a longitudinally adjustable valve shaft extending axially through said drive shaft and having a slidable straight spline rotary drive connection with said coupling sleeve, a slidable helical spline rotary drive connection between said shafts, a spring-loaded mechanism acting against said sleeve in a direction to increase said quantity of pump delivery, a control pin 'extending slidably through said valve shaft for engagement with said coupling sleeve, centrifugal means rotatable with said drive shaft and acting on said pin in a direction to decrease said quantity of pump delivery, an abutment on and movable axially with said valve shaft, a spring-loaded mechanism acting against said abutment in a direction to retard the phase relation of said valve shaft to said drive shaft through the action of said helical spline connection, and centrifugal means rotatable with said drive shaft and acting on said valve shaft in opposition to said last mentioned springloaded mechanism.

15. A pump mechanism comprising, in combination, a pump having a drive element and having a control element adjustable to vary the quantity of pump delivery, means for automatically adjusting said control element to vary the phase relation of the time of pump delivery to the position of said drive element in response to the o perating speed of said pump, and means adjustable in synchronism with said last mentioned means and operable to limit the adjustment of saidcontrol element for maximum delivery.

16. A pump mechanism comprising, in combination, a pump having a rotary control element axially adjustable to vary the quantity of pump delivery, an axially adjustable drive shaft having an axially adjustable rotary drive connec- -tion with said element, a stop for limiting adjustment of said element in one direction, spring actuated means tending to move said shaft in one axial direction, centrifugal means rotatable in synchronism with said shaft and tending to move said shaft in the other direction, and means controlled by said spring actuated means for determining the position of said stop in response to the operating speed of said pump.

17. A pump mechanism comprising, in combination, a pump having a rotary control element axially adjustable to vary the quantity of pump delivery, 'a drive shaft having an axially adjustable rotary drive connection with said element, a stop for limiting adjustment of said element in one direction, a lever acting against said shaft in one axial direction and carrying a limit control cam, spring means for actuating said lever, centrifugal means responsive to the rotative speed of said shaft acting in opposition to said lever, and a lever coasting with said cam to con trol the position of said stop in response to the operating speed of said pump.

18. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity of delivery, means including an actuating member for adjusting said element, a pneumatic governor for controlling the position of said member, and means adjustable in response to changes in speed of said pump for limiting movement of said member in one direction.

19. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity of delivery, means including an actuating member for adjusting said element, a cam for adjusting said member, a pneumatic governor for controlling said cam, and a second cam automatically adjustable in response to the operating speed of said pump for limiting the maximum permissible extent of adjustment of said member in accordance with said speed.

20. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity of delivery, a cam for limiting the adjustment of said .element in one direction, a second cam for controlling the adjustment of said element within said limit, and means for operating said second cam.

21. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity of delivery, governor means for adjusting said element, and means automatically operable in response to the operating speed of said pump for modifying the adjustment of said element independently of said governor means and in accordance with said speed. p

22. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity of delivery, a 'cam mounted for rotation and for swinging movement and controlling the position of adjustment'of said element, means for rotating said cam to adjust said element, and means for swinging said cam to adjust said element.

23. A pump mechanism comprising, in combination, a pump having a control element adjustable to vary the quantity, of -delivery, a cam mounted for rotation and for swinging movement and controlling the position of adjustment t of said element, pneumatic governor means for rotating said cam to adjust said element, and pump speed responsive means for swinging said cam to adjust said element in a direction to increase said quantity upona decrease in said speed. 24. 'A pump mechanism comprising, in combination, a pump having a rotary control element axially adjustable to vary the quantity of pump delivery, spring means tending to move said element in a direction to increase said quantity, a stop member hunting the position of said element against the action of said spring means, means responsive to the operating speed of said pump for limiting the position of said member to determine the maximum permissible delivery at any speed, means for adjustably limiting the positionV of said member independently of said rst mentioned means, and two separate means for independently actuating said last mentioned means.

25. A pump mechanism comprising, in combination, a pump having av rotary control element axially adjustable to vary the quantity of pump delivery, spring means tending to move said element in a direction to increase said quantity, a stop member limiting the position of said element against the action of said spring means, and a plurality of independent means selectively operabile to adjust the position of said stop member.

26. A pump mechanism comprising in combination, a pumping unit having a drive element, means including a first governor responsive to the pump speed for automatically controlling the quantity of pump delivery, means` including a second governor responsive to the pump speed independently of said rst governor for automat- `ically controlling the phase relation of the time of said delivery to the position of said drive element, and a stop member adjustable by said Isecond' governor and disposed in cooperative relation to said first mentioned means to limit the maximum quantity of pump delivery obtainable by 'control by said rst mentioned means at different pump speeds, while permitting independent control of the quantity of pump delivery by said rst mentioned means below said maximumv quantity.

CARROLL R. ALDEN.

Cil 

